JPS60249687A - Rotary type hydraulic machine - Google Patents

Abstract

PURPOSE:To lessen machining errors in a scroll body as well as to make the machining time reducible, by making up the scroll body into an involute form, and forming a constant radial circular arc in the inward, while connecting contact points of two curves so smoothly. CONSTITUTION:A fixed scroll body and a movable scroll body consisting of each of the same formed scroll bodies, being engaged with each other in a slip of 180 deg., are constituted so as to make the movable side revolvable at a constant radius psi to the fixed side. Both these scroll bodies are made up of an inner side curve 702 consisting of an involute outer side curve 701 and a circular arc of a radius R and a circular arc of a radius (r) connecting body these curves. These radii R and (r) are prescribed as in an expression I, provided they are set to a base radius of the involute curve.

Description

[Detailed description of the invention] [Industrial application field] The present invention relates to a rotary fluid machine.

[Conventional technology]

For example, in a known scroll compressor, one of two spiral bodies having the same shape, as shown in FIG.
is fixed to a seal end plate having a discharge port 4 approximately in the middle, and both are rotated 180 degrees relative to each other, and the spiral bodies of both are in contact with each other at four points 51, 52, 51', and 52'. As such, the distance 2ρ(-Uzumaki Pinochi 2×
The spiral body 2 is stacked on top of each other at a relative distance of the spiral plate thickness), one spiral body 2 is kept stationary, and the other spiral body 1 is rotated by a crank mechanism having a crank radius ρ. Rotate around the center O of (
It is configured to revolve around a radius ρ==Q o'.

Then, between the two spiral bodies 1.2, sealed small chambers 3, 3 are formed between the points 51, 52 where both the spiral bodies abut and between the points 51' and 52'. The volume of spiral body 3 changes gradually as the spiral body l revolves.
When it revolves at 0 degrees, it becomes (2) in the same figure, when it revolves at 180 degrees, it becomes (3) in the same figure, and when it revolves at 270 degrees, it becomes (4) in the same figure.
During this period, the volume of small chamber 3 gradually decreases, as shown in the figure (
In 4), the two small chambers 3°3 are connected to form /''-chamber 53, and when the state of the figure (4) is further revolved by 90 degrees, it becomes the figure (1), and the volume of the small chamber 53 is as shown in the figure (2). ) from the same figure (
3), and the volume becomes the smallest between (3) and (4) in the same figure, and during this time, the outer space that began to open in (2) in the same figure increases in (3) and (4) in the same figure. Figures (4) to (1)
Then, new gas is taken in to form a sealed/JX chamber, and this process is repeated thereafter, and the gas taken in from the spiral outer body space is compressed and discharged from the discharge port 4.

The above is the operating principle of the scroll type compressor. Specifically, as shown in the vertical cross-sectional view of FIG.
Rear end plate 12. Consisting of a cylinder plate 13, an intake port 14 and a discharge port 15 on the rear end plate 12.
When protruding, the spiral body 252 and the disc 25
The main shaft 1 has a stationary scroll member 25 fixed thereon, and has a crank bin 23 on the front end plate 11.
7, and attach it to the crank pin 23 as shown in Fig. 4 (I in Fig. 3).
As shown in V'-IV sectional view), the radial needle bearing 26. Boss 243 of the revolving scroll member 24. Square tube member 271. The revolving scroll member 2 consisting of the spiral body 242 and the disk 241 is rotated through the revolving mechanism consisting of the sliding body 291, the 1,1 ring member 2922, the detent 293, etc.
4 is attached.

The shape of the spiral bodies 1 and 2 of such a scroll type compressor is determined by, for example, the outside of the spiral body, as described in detail in Japanese Patent Application No. 1976-1972 proposed by the present inventors. And most of the inner curve can be composed of an implicit function, but as described in the operating principle, the small chamber 53 gradually decreases its volume, and as a result, high-pressure fluid is discharged from the discharge port. When the spiral body has a thickness, the volume of the small chamber does not become zero, and there is a phenomenon in which a so-called top clearance volume remains.

That is, as shown in the enlarged view of the fifth hair part, (1)
corresponds to Fig. 1 (3), and two spiral bodies 1,202
lJS chamber 53 formed between two contact points 52 and 52'
When the spiral body 1 further revolves, it becomes as shown in the same figure (2), and the volume of the small chamber 53 becomes the minimum due to the tiles.When the spiral body 1 further revolves, the two spiral bodies 1 and 2 are separated, and the contact point is 52°52 The small chamber 53 formed between the two spiral bodies 1 and 2 communicates with the small chambers 3 and 3 formed on the outside of each spiral body.

Therefore, the high-pressure fluid in the minimum volume of the small chamber shown in FIG. The work done by the compressor on the fluid becomes loss.

Further, since the tips of the central portions of the spiral bodies 1 and 2 each have sharp edges, these portions may be damaged during operation, and furthermore, the number of man-hours required for machining the tip portions is increased.

In order to solve this problem, the present inventors previously proposed a rotary fluid machine equipped with a spiral body as shown in the 6th front view in Japanese Patent Application No. 57-206088.

That is, in the same figure, 501 is a fixed side spiral body,
601 and 602 are the outer and inner curves of the spiral body 501, respectively, where the outer curve 601 has a radius of the base circle, an involute curve to the starting point, and the EF of the inner curve 602 has an angle π-■ phase difference with the outer curve 601. The shifted involute curve, DB is a circular arc with radius R, and the outer curve is 60
1 and the inner curve 602 has a radius r
Point A is the involute starting point of the outer curve 601, Point B is the boundary point between the outer curve 601 and the connecting curve 603, and the tangents of both curves are equal at this point.Point C
is a point sufficiently outside the outer curve 601, and the point is the inner curve 60
2 and the connecting curve 603, the two circular arcs of radii R and r touch at this point, and the point E is the boundary point of the inner curve 602 (D
B) and the involute curve EF, the two curves have their respective tangents equal at this point, and the point F is the inner curve 6
This is a point well outside of 02.

The same applies to the other revolution side spiral body 502.

In this case, the radius R9r is expressed by the following formula.

R=ρ+bβ10d・・・・・・・・・・・・・・・
・・・・・・・・・ (1) r = bβ+d ・・・・
・・・・・・・・・・・・・・・・・・・・・・・・
・ (2) Then, ρ: Radius of revolution b = Radius of base circle b"-(-+bβ)' d = -... (3) 2(-10bβ) β = parameter.

The parameter β is equal to the angle between the straight line passing through the origin 0 and the negative X axis, and the two intersections of the straight line passing through the origin 0 and the base circle with the angle β are on the straight line EO2 and the straight line Bo3, and the straight line EO,
and straight line BO, are in contact with the base circle at the above-mentioned intersection.

Next, in FIG. 7, 502 is a spiral body on the revolution side;
52 and 552' are contact points of both spiral bodies, 5
53 is a small chamber formed at contact points 552° and 552';
03.503 are the outer chambers, and (1) in the same figure is
FIG. 5(1) and FIG. 5(2) respectively correspond to FIG. 5(2), and FIG. The following are the cases in which the two objects are further revolved.

In this proposal, both spiral bodies 501 and 502 are relatively as shown in Fig. 7 (1), (2), (3), (4),
When the revolution is performed in the order of (5), the contact points 552, 5
The volume of the small chamber 553 formed by 52' decreases, and the volume of the small chamber 553 formed in the same figure (
In 5), the contact points 552 and 552' become the same point, and the volume of the small chamber 553 becomes zero.

For this reason, the so-called top clearance volume that existed conventionally becomes zero, and all of the fluid compressed from this volume is discharged to the outside from the discharge port (not shown), and all of the work that the compressor applies to the fluid is transferred to the fluid. The losses that previously existed will disappear.

In the above embodiment, the size of the discharge port has been ignored for convenience of explanation, but in reality, it is necessary to form the discharge port at an appropriate position where the small chamber 553 is formed, so this allows for some top clearance. Although a volume is generated, this amount is much smaller than in the conventional case and can be considered as substantially zero.

As shown in Fig. 6, the shape of the tip of the central part of each of the spiral bodies 501.5'02 is a connecting curve 603 of a circular arc, thereby eliminating sharp edges and preventing damage to this part during operation of the machine. There is no inner curve 6
02 and the connection curve 603 are circular arcs, making it easy to process the spiral body.

According to the above proposal, many drawbacks can be solved and great effects can be obtained, but on the other hand, the following disadvantages may occur.

In other words, the shape of the spiral body is determined by three factors: the involute-1-base circle radius b, the radius of gyration ρ, and the parameter β (representing the involute establishment limit), but in machining an actual machine, it is usually When an end mill cutter is used, it is necessary to consider the diameter of this end mill cutter, and in Japanese Patent Application No. 57-206088, it is necessary to use a thin end mill cutter because it is limited by the radius of curvature R between the circular arc portions BD. In this case, machining errors and machining time increase due to insufficient rigidity of the end mill cutter.

The present invention has been proposed in view of the above circumstances, and it is possible to use an end mill cutter with a diameter that is the same as or slightly smaller than the groove width of the spiral body. The objective is to provide a rotary fluid machine that reduces machining time.

[Means for solving problems]

To this end, in the present invention, the stationary side spiral body and the revolution side spiral body, which are spiral bodies of the same shape, are rotated 180 degrees with each other so that the revolution side spiral body revolves with a revolution radius ρ relative to the stationary side spiral body. In a product, each of the spiral bodies has an outer curve made of an involute curve, an inner curve made of an involute curve having an arc of radius R inward, and a radius smoothly connecting the outer curve and the arc of radius R. Formed by the arc of , −) base circle radius of the curve).

[For production]

According to such a configuration, it is possible to obtain a high-performance, low-cost rotary fluid machine in which the machining time is shortened by reducing the machining error by /h.

〔Example〕

An embodiment of the present invention will be described with reference to the drawings. FIG. 1 is a front view showing the spiral body.

In the above figure, the same symbols as in Fig. 6 indicate the same parts and dimensions as in the same figure, and R, r, and d are respectively the same as (
1) is the same as equations (2) and (3), and parameter β satisfies the relationship of equation (4).

701 is the outer curve of the fixed side spiral body 505, 702 is its inner curve, the outer curve 701 is an involute curve to the starting point on the base circle radius, and the space between 82 of the inner curve 702 and the outer curve 701 is an angle π-■. Inpoly with phase shift.

- curve, DE is between radius R center 0 given by equation (1)
20 circular arcs, the connecting curve 703 connecting the outer curve 701 and the inner curve 702 has a radius r center 0 given by equation (2)
1 arc, point A is the involute starting point (base circle radius b) of the outer curve 701, point B is the outer curve 701 and the connecting curve 70
At the boundary point of 3, both curves have their tangents equal at this point.

Point C is a point sufficiently outside the outer curve 701, and the point is a boundary point between the inner curve 702 and the connecting curve 703, where the two circular arcs of radius R and radius r touch.

Point E is a boundary point between the arc (between DE) of the inner curve 702 and the involute curve EF, and the tangents of both curves are made equal. Point F is a point well outside the inner curve 702.

Here, the parameter β is the angle between the straight line passing through the origin 0 and the negative direction of the Straight line BO.

The straight line EO2 and the straight line BO, touch the base circle at the above-mentioned intersection, and BO2 and BO- are parallel.

The same applies to the spiral body on the revolution side.

In such a spiral body, the groove width T. is (5
) is given by the formula.

T, = πb + ρ ・・・・・・・・・・・・・・・・・・
・・・・・・・・・ (5) Therefore, the parameter is (4
), the radius R of the arc portion of the inner curve is R>T, ・・・・・・・・・・・・・・・・・・
・・・・・・・・・・・・・・・・・・ (6)

According to such a spiral body, the groove width of the spiral body is T6.
Since it is possible to process between the groove and the circular arc ED using a cutter with an end mill cutter diameter that is approximately equal to or slightly smaller than The inconveniences that sometimes occur will be resolved.

In addition, in the above-mentioned example, the following modification example can be considered.

(1) Instead of the inner curve 7020, the inner curve 710 may be constructed by providing a slight clearance ΔC, that is, a relief margin ΔC, as shown by a broken line in the figure on the side of the outer curve 701 than the inner curve 702.

Here, point G is an arbitrary point between the dot on the connection curve and point B, and for convenience of explanation, point G is a relatively large ΔC.
is shown in the figure, but the amount of ΔC may be determined by the lessee.

(2) Although not shown, instead of providing the clearance ΔC on the inner curve in (1) above, it is of course possible to provide a clearance ΔC on the connecting curve to take the clearance.

(3) One spiral body has the shape of the above example, and only the other spiral body is provided with a gap △C on both the inner curve and the outer curve, which is the combination of (]) and (2) above. It is also possible to compose a fee.

(4) A slight gap may be provided between the inner and connecting curves of both spiral bodies.

In any of the above cases (1) to (4), since △C is up to a slight gap, the effect intended in Japanese Patent Application No. 57-206088 is achieved without loss, and the machine has good efficiency. It is possible to provide

(5) The present invention is not limited to compressors, but can be widely applied to any fluid machine having a spiral body, regardless of its use.

〔Effect of the invention〕

In short, according to the present invention, the stationary side spiral body and the revolution side spiral body, which are spiral bodies of the same shape, are rotated 180 degrees with each other so that the revolution side spiral body revolves with the revolution radius ρ with respect to the stationary side spiral body. In this, both spiral bodies are each smoothly connected to an outer curve made of an involute curve, an inner curve made of an involute curve having an arc of radius R inward, and the outer curve and the arc of radius R. It is formed by a circular arc of radius r (tag, R2ρ+β+d r=bβ+d b2−(−+bβ)′ d = −, −−−−−−−−− 2(− +bβ) b = base circle radius of involito curve) to obtain a low-cost, high-performance rotary fluid machine that reduces machining errors by using a relatively large-diameter end mill cutter and shortens machining time. I can do it.

[Brief explanation of drawings]

FIG. 1 is a front view showing a spiral body according to an embodiment of the present invention;
Figure 2 is a diagram of the operating principle of a known scroll compressor;
The figure is a longitudinal cross-sectional view showing a known scroll type compressor, FIG. 4 is a cross-sectional view taken along IV-IV in FIG. 3, and FIG.
Figure 6 is a front view showing the spiral body proposed in Japanese Patent Application No. 57-20608, and Figure 7 is the spiral body shown in Figure 6. FIG. 3 is a partially enlarged cross-sectional view showing changes in the relative position of both spiral bodies of a scroll compressor equipped with the scroll type compressor. 505...Fixed side spiral body 1.701...Outer curve, 702...Inner curve, 703...Connection curve b...
・Base circle radius of involute curve, △C... Clearance,
β...Parameter, Rl r...Radius, T,...
Groove width, A...Start point, B...Boundary point, C...Point sufficiently outside, D...Pa boundary point, E...Boundary point, F...Point sufficiently outside. Sub-Agent Patent Attorney Tadashi Tsukamoto Writer Figure 1 Figure 2 (1) (2) Figure 3 0 Figure 4; rn 291 Figure 5 (1) (2)

Claims (1)

[Scope of Claims] The stationary side spiral body and the revolving side spiral body, each consisting of a spiral body having the same shape, are rotated 180 degrees to mesh with each other so that the revolution side spiral body revolves with a revolution radius ρ relative to the stationary side spiral body. In this, both spiral bodies each have an outer curve made of an involute curve, an inner curve made of an involute curve having an arc of a radius hole inward, and a radius r that smoothly connects the outer curve and the arc of the radius hole. (Ty, R
=ρ+bβ+d r = bβ+d b2−(L−4−bβ)′ d == , −, −−−−−−−−−−−2(−+b
β) A rotary fluid machine characterized by b: base circle radius of involito curve).